JPH0828506A - Pressure compensating valve - Google Patents
Pressure compensating valveInfo
- Publication number
- JPH0828506A JPH0828506A JP15992694A JP15992694A JPH0828506A JP H0828506 A JPH0828506 A JP H0828506A JP 15992694 A JP15992694 A JP 15992694A JP 15992694 A JP15992694 A JP 15992694A JP H0828506 A JPH0828506 A JP H0828506A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- port
- spool
- load
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
- F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
- G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87169—Supply and exhaust
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、建設機械における１つ
又は複数の油圧ポンプの吐出圧油を複数のアクチュエー
タに流量分配して供給する油圧回路等に用いられる圧力
補償弁に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure compensating valve used in a hydraulic circuit or the like of a construction machine, in which hydraulic oil discharged from one or a plurality of hydraulic pumps is distributed to a plurality of actuators in a flow rate distribution manner.
【０００２】[0002]
【従来の技術】１つの油圧ポンプの吐出圧油を複数のア
クチュエータに供給すると、負荷圧の低いアクチュエー
タにのみ圧油が供給されてしまうので、これを解決する
手段として例えば特開昭６０−１１７０６号公報に示す
油圧回路が知られている。すなわち各アクチュエータに
接続した方向制御弁の入口側に圧力補償弁をそれぞれ設
け、各圧力補償弁の各アクチュエータの負荷圧における
最も高い負荷圧でセットし、異なる負荷圧の複数のアク
チュエータに油圧ポンプの吐出圧油を流量分配して供給
できるようにした油圧回路である。2. Description of the Related Art When the pressure oil discharged from one hydraulic pump is supplied to a plurality of actuators, the pressure oil is supplied only to the actuator having a low load pressure, and as a means for solving this, for example, Japanese Patent Laid-Open No. 60-11706. The hydraulic circuit shown in Japanese Patent Publication is known. That is, a pressure compensating valve is provided on the inlet side of the directional control valve connected to each actuator, set at the highest load pressure of the load pressure of each actuator of each pressure compensating valve, and the hydraulic pumps are set to the multiple actuators of different load pressures. This is a hydraulic circuit that allows the discharge pressure oil to be distributed and supplied.
【０００３】かかる圧力補償弁としては、例えば特願平
３−２９０９９号に示すものが知られている。つまり、
図１に示すように弁本体１に入口ポート２と出口ポート
３を連通・遮断する弁４を設けてチェック弁部５とし、
前記弁本体１に、第１ポート６に連通した第１圧力室７
の圧力で第２ポート８と第３ポート９を連通し、第３ポ
ート９に連通した第２圧力室１０の圧力で第２ポート８
と第３ポート９を遮断するスプール１１を設けて減圧弁
部１２とし、前記スプール１１をばね１３で第２ポート
８と第３ポート９を遮断する方向に押して前記弁４に当
接した圧力補償弁。As such a pressure compensating valve, for example, one disclosed in Japanese Patent Application No. 3-29099 is known. That is,
As shown in FIG. 1, the valve body 1 is provided with a valve 4 that connects and disconnects the inlet port 2 and the outlet port 3 to form a check valve portion 5,
The valve body 1 has a first pressure chamber 7 communicating with the first port 6.
The second port 8 and the third port 9 are communicated with each other under the pressure of, and the second port 8 is communicated with the pressure of the second pressure chamber 10 communicated with the third port 9.
And a spool 11 for shutting off the third port 9 is provided as a pressure reducing valve portion 12, and the spool 11 is pressed by a spring 13 in a direction for shutting off the second port 8 and the third port 9 so as to compensate for pressure contacting the valve 4. valve.
【０００４】かかる圧力補償弁であると、第１圧力室７
の圧力が第２圧力室１０の圧力よりも高い時にはスプー
ル１１が弁４より離れて入口ポート２の圧力と出口ポー
ト３の圧力が等しくなると共に、第１圧力室７の圧力と
第２圧力室１０の圧力が等しくなり、第１圧力室７の圧
力が第２圧力室１０の圧力よりも低い時にはスプール１
１で弁４が遮断方向に押されて出口ポート３の圧力が入
口ポート２の圧力よりも第２圧力室１０と第１圧力室７
の圧力差だけ低くなる。With such a pressure compensating valve, the first pressure chamber 7
Is higher than the pressure in the second pressure chamber 10, the spool 11 is separated from the valve 4 so that the pressure at the inlet port 2 becomes equal to the pressure at the outlet port 3, and the pressure in the first pressure chamber 7 and the pressure in the second pressure chamber When the pressures in the first pressure chamber 7 are lower than the pressure in the second pressure chamber 10, the spool 1
The valve 4 is pushed in the shut-off direction by 1 so that the pressure at the outlet port 3 becomes greater than the pressure at the inlet port 2 in the second pressure chamber 10 and the first pressure chamber 7.
The pressure difference will be lower.
【０００５】このようであるから、出口ポート３を方向
制御弁１４のポンプポート１５に接続し、第１ポート６
を方向制御弁１４の出力ポート１６に接続して自己の負
荷圧Ｐ1 を第１圧力室７に導入し、第３ポート９を負荷
圧検出路１７に接続して制御圧ＰLSを第２圧力室１０に
導入すると共に、油圧ポンプ１８の吐出路１９を入口ポ
ート２と第２ポート８に連通することで、ポンプ吐出圧
Ｐ0 を制御圧ＰLSと自己の負荷圧Ｐ1 の差圧（ＰLS−Ｐ
1 ）だけ減圧して出力ポート３に出力できる。例えばＰ
0 ＝１２０ｋｇ／ｃｍ2 、ＰLSとＰ1 が１００ｋｇ／ｃ
ｍ2 の時には出力圧Ｐ2 は１２０ｋｇ／ｃｍ2 となり、
Ｐ0 ＝１２０ｋｇ／ｃｍ2 ，Ｐ1 ＝１０ｋｇ／ｃｍ2 ，
ＰLS＝１００ｋｇ／ｃｍ2 の時には出力圧Ｐ2 が３０ｋ
ｇ／ｃｍ2 となる。Because of this, the outlet port 3 is connected to the pump port 15 of the directional control valve 14, and the first port 6
Is connected to the output port 16 of the directional control valve 14 to introduce its own load pressure P 1 into the first pressure chamber 7, and the third port 9 is connected to the load pressure detection path 17 to control the control pressure P LS to the second. By introducing the discharge passage 19 of the hydraulic pump 18 to the inlet port 2 and the second port 8 while introducing it into the pressure chamber 10, the pump discharge pressure P 0 is a differential pressure between the control pressure P LS and its own load pressure P 1 . ( PLS- P
Only 1 ) can be decompressed and output to output port 3. For example P
0 = 120 kg / cm 2 , P LS and P 1 are 100 kg / c
At m 2 , the output pressure P 2 is 120 kg / cm 2 ,
P 0 = 120 kg / cm 2 , P 1 = 10 kg / cm 2 ,
When P LS = 100 kg / cm 2 , the output pressure P 2 is 30 k
It becomes g / cm 2 .
【０００６】[0006]
【発明が解決しようとする課題】かかる圧力補償弁は例
えば図２に示すように、１つの油圧ポンプ１８の吐出路
１９に設けられた複数の方向制御弁１４の入口側にそれ
ぞれ設けられ、各第３ポート９を負荷圧検出路１７で連
通して各第２圧力室１０には各圧力補償弁の自己の負荷
圧Ｐ1 、つまり各アクチュエータ２０の負荷圧における
最も高い圧力が作用するようにしている。なお、図２に
おいて圧力補償弁は模式的に表現してある。Such a pressure compensating valve is provided on each inlet side of a plurality of directional control valves 14 provided on the discharge passage 19 of one hydraulic pump 18, as shown in FIG. The third port 9 is communicated with the load pressure detection path 17 so that the self load pressure P 1 of each pressure compensating valve, that is, the highest pressure of the load pressure of each actuator 20 acts on each second pressure chamber 10. ing. The pressure compensating valve is schematically shown in FIG.
【０００７】図２に示す油圧回路において複数の方向制
御弁１４を同時操作して各アクチュエータ２０を同時操
作する時に、１つのアクチュエータ２０がストロークエ
ンドになるとその方向制御弁１４のメータイン開口部に
圧油が流れずに油圧ポンプ１８のポンプ吐出圧Ｐ0 が主
リリーフ弁２１のセット圧まで上昇し、そのストローク
エンドになったアクチュエータ２０の負荷圧Ｐ1 がポン
プ吐出圧Ｐ0 と等しくなり、負荷圧ＰLSもポンプ吐出圧
Ｐ0 と等しくなる。つまり、第２ポート８と第３ポート
９が直接連通するために負荷圧ＰLSとポンプ吐出圧Ｐ0
が等しくなる。In the hydraulic circuit shown in FIG. 2, when a plurality of directional control valves 14 are simultaneously operated to simultaneously operate each actuator 20, when one actuator 20 reaches the stroke end, a pressure is applied to the meter-in opening of the directional control valve 14. The pump discharge pressure P 0 of the hydraulic pump 18 rises to the set pressure of the main relief valve 21 without oil flowing, and the load pressure P 1 of the actuator 20 at the end of its stroke becomes equal to the pump discharge pressure P 0. The pressure P LS also becomes equal to the pump discharge pressure P 0 . That is, since the second port 8 and the third port 9 are in direct communication, the load pressure P LS and the pump discharge pressure P 0
Are equal.
【０００８】このために、ストロークエンドに達してい
ない他のアクチュエータ２４に接続した圧力補償弁の第
２圧力室１０に前記主リリーフ弁２１のセット圧が作用
し、その第１圧力室７には主リリーフ弁２１のセット圧
よりも低い自己の負荷圧Ｐ1が作用してスプール１１が
圧力補償弁のチェック弁部５を構成する弁４を入口ポー
ト２と出口ポート３を遮断方向に押し、入口ポート２と
出口ポート３が遮断するのでストロークエンドに達して
いない他のアクチュエータ２４に圧油を供給できないか
ら、他のアクチュエータ２０が停止してしまう。For this reason, the set pressure of the main relief valve 21 acts on the second pressure chamber 10 of the pressure compensation valve connected to the other actuator 24 which has not reached the stroke end, and the first pressure chamber 7 thereof The self-load pressure P 1 lower than the set pressure of the main relief valve 21 acts to cause the spool 11 to push the valve 4 constituting the check valve portion 5 of the pressure compensation valve in the closing direction of the inlet port 2 and the outlet port 3, Since the inlet port 2 and the outlet port 3 are blocked, the pressure oil cannot be supplied to the other actuator 24 that has not reached the stroke end, so that the other actuator 20 stops.
【０００９】図２において、２２は油圧ポンプ１８の吐
出流量を制御する斜板、２３はサーボシリンダ、２４は
ポンプ斜板角制御弁であり、このポンプ斜板角制御弁２
４はポンプ吐出圧Ｐ0 と負荷圧ＰLSとの差圧によって切
換え作動してポンプ吐出圧をサーボシリンダ２３に供給
して斜板２５の角度を変更してポンプ吐出圧Ｐ0 と負荷
圧ＰLSの差圧を常に一定としている。なお、負荷圧検出
路１７は絞り２５でタンク２６に接続してある。In FIG. 2, 22 is a swash plate for controlling the discharge flow rate of the hydraulic pump 18, 23 is a servo cylinder, and 24 is a pump swash plate angle control valve.
Reference numeral 4 denotes a pressure difference between the pump discharge pressure P 0 and the load pressure P LS, which is switched to supply the pump discharge pressure to the servo cylinder 23 and change the angle of the swash plate 25 to change the pump discharge pressure P 0 and the load pressure P 4. The differential pressure of LS is always constant. The load pressure detection path 17 is connected to the tank 26 by a throttle 25.
【００１０】そこで本発明は前述の課題を解決できるよ
うにした圧力補償弁を提供することを目的とする。Therefore, an object of the present invention is to provide a pressure compensating valve capable of solving the above-mentioned problems.
【００１１】[0011]
【課題を解決するための手段】油圧ポンプ１８の吐出圧
油が供給される入口ポート３４と方向制御弁１４の入力
側に接続される出口ポート３５の開口面積を制御する弁
３６を有するチェック弁部３８と、第１圧力室４４に供
給される自己の負荷圧Ｐ1 によって前記弁３６の開口面
積増方向の摺動を許容する一方向に摺動し、第２圧力室
４５内の圧力で前記弁３６を開口面積減方向に押す他方
向に摺動するスプール４３と、このスプール４３の内部
に形成され、スプール４３が一方向に所定ストローク以
上摺動すると前記第２圧力室４５に油圧ポンプ１８の吐
出圧油を供給する内部通路６１と、この内部通路６１
を、絞り２５でタンク２６に接続した負荷圧検出路１７
に連通する絞り６２より成る減圧弁部６３より構成した
圧力補償弁。A check valve having an inlet port 34 to which hydraulic oil discharged from a hydraulic pump 18 is supplied and an outlet port 35 connected to an input side of a directional control valve 14 for controlling the opening area of a valve 36. The portion 38 and its own load pressure P 1 supplied to the first pressure chamber 44 cause the valve 36 to slide in one direction that allows sliding in the direction of increasing the opening area, and the pressure in the second pressure chamber 45 A spool 43 that slides in the other direction that pushes the valve 36 in the direction of decreasing the opening area, and a spool 43 that is formed inside the spool 43 and that slides in one direction for a predetermined stroke or more to the second pressure chamber 45. The internal passage 61 for supplying the discharge pressure oil of 18 and the internal passage 61
Is connected to the tank 26 with the throttle 25, and the load pressure detection path 17
A pressure compensating valve composed of a pressure reducing valve portion 63 composed of a throttle 62 communicating with the.
【００１２】[0012]
【作 用】第２圧力室４５内の圧油は絞り６２を通っ
て負荷圧検出路１７に流出し、その圧油の一部は負荷圧
検出路１７の絞り２５を経てタンク２６に流出するから
絞り６２の前後に圧力差が生じ、負荷圧検出路１７の負
荷圧ＰLSは第２圧力室４５の圧力よりも低圧となる。こ
れにより１つの油圧ポンプの吐出圧油を複数の方向制御
弁によって各アクチュエータに供給する油圧回路におけ
る各方向制御弁の入口側に圧力補償弁をそれぞれ設け、
その各負荷圧検出路１７を連通して各圧力補償弁が最も
高い負荷圧によってセットされるようにした場合に、１
つのアクチュエータがストロークエンドになってポンプ
吐出圧Ｐ0 と自己の負荷圧Ｐ1 が等しくなっても負荷圧
ＰLSがポンプ吐出圧Ｐ0 より低くなるからストロークエ
ンドに達しない他のアクチュエータの圧力補償弁におけ
る減圧弁部６３の第２圧力室４５内の圧力はポンプ吐出
圧Ｐ0 より低圧となり、その圧力補償弁のチェック弁部
の弁３６が閉じることがないので他のアクチュエータに
ポンプ吐出圧油を供給できる。[Operation] The pressure oil in the second pressure chamber 45 flows out to the load pressure detection passage 17 through the throttle 62, and a part of the pressure oil flows out to the tank 26 via the throttle 25 in the load pressure detection passage 17. Therefore, a pressure difference occurs before and after the throttle 62, and the load pressure P LS of the load pressure detection path 17 becomes lower than the pressure of the second pressure chamber 45. As a result, a pressure compensating valve is provided on the inlet side of each directional control valve in the hydraulic circuit that supplies the discharge pressure oil of one hydraulic pump to each actuator by a plurality of directional control valves.
When the load pressure detection paths 17 are communicated with each other so that each pressure compensation valve is set by the highest load pressure, 1
Even if one actuator reaches the stroke end and the pump discharge pressure P 0 and its own load pressure P 1 become equal, the load pressure P LS becomes lower than the pump discharge pressure P 0 , so the pressure does not reach the stroke end. The pressure in the second pressure chamber 45 of the pressure reducing valve portion 63 of the valve becomes lower than the pump discharge pressure P 0 , and the valve 36 of the check valve portion of the pressure compensating valve does not close, so pump discharge pressure oil to other actuators. Can be supplied.
【００１３】[0013]
【実 施 例】図３に示すように、弁本体３１には一側
孔３２と他側孔３３が相対向して形成され、その一側孔
３２には入口ポート３４と出口ポート３５が形成してあ
ると共に、弁３６が嵌挿され、その弁３６はプラグ３７
で図示位置より左方に摺動しないように規制されてチェ
ック弁部３８を構成している。[Example] As shown in FIG. 3, a valve body 31 is formed with one side hole 32 and another side hole 33 facing each other, and an inlet port 34 and an outlet port 35 are formed in the one side hole 32. At the same time, the valve 36 is inserted and the valve 36 is plugged in.
The check valve portion 38 is configured so as not to slide to the left from the illustrated position.
【００１４】前記他側孔３３には第１・第２・第３ポー
ト４０，４１，４２が形成されていると共に、スプール
４３が嵌挿されて第１ポート４０に開口した第１圧力室
４４と第３ポート４２に連通・遮断する第２圧力室４５
を構成し、そのスプール４３はプラグ４６との間に設け
たばね４７で左方に押されてスプール４３に一体的に設
けた押杆４８が透孔４９より突出して前記弁３６をプラ
グ３７に当接している。First, second, and third ports 40, 41, 42 are formed in the other side hole 33, and a first pressure chamber 44, into which the spool 43 is fitted and opened at the first port 40. And the second pressure chamber 45, which connects and disconnects with the third port 42
The spool 43 is pushed to the left by a spring 47 provided between it and a plug 46, and a pushing rod 48 integrally provided on the spool 43 projects from a through hole 49 so that the valve 36 abuts on the plug 37. Touching.
【００１５】前記スプール４３の盲穴５０にロードピス
トン５１が嵌挿されて盲穴５０の底部寄りに受圧室５２
を形成し、この受圧室５２は径方向の第１孔５３により
スプール４３の第１小径部５４に開口して受圧室５２は
第２ポート４１に常時連通している。前記ロードピスト
ン５１には軸方向の油孔５５が形成され、この油孔５５
は径方向の第２孔５６で第２圧力室４５に常時連通して
いると共に、径方向の第３孔５７と小径部５８で外周面
に開口し、その小径部５８はピストン４３に形成した径
方向の第４孔５９、第２小径部６０で第３ポート４２に
常時連通し、第１小径部５４と第１孔５３と受圧室５２
と小径部５８と第３孔５７と油孔５５と第２孔５６でス
プール４３内部に第２ポート４１と第２圧力室４５を連
通する内部通路６１を形成し、その内部通路６１は細孔
等の絞り６２と第４孔５９を経て第３ポート４２に連通
して減圧弁部６３を構成している。A load piston 51 is fitted into the blind hole 50 of the spool 43 so that the pressure receiving chamber 52 is located near the bottom of the blind hole 50.
The pressure receiving chamber 52 is opened to the first small diameter portion 54 of the spool 43 by the first hole 53 in the radial direction, and the pressure receiving chamber 52 is always in communication with the second port 41. An axial oil hole 55 is formed in the load piston 51.
Is always in communication with the second pressure chamber 45 through a second radial hole 56, and is open to the outer peripheral surface through a third radial hole 57 and a small diameter portion 58, and the small diameter portion 58 is formed on the piston 43. The fourth hole 59 and the second small diameter portion 60 in the radial direction are in constant communication with the third port 42, and the first small diameter portion 54, the first hole 53, and the pressure receiving chamber 52.
The small diameter portion 58, the third hole 57, the oil hole 55, and the second hole 56 form an internal passage 61 that connects the second port 41 and the second pressure chamber 45 inside the spool 43, and the internal passage 61 is a fine hole. The pressure reducing valve section 63 is formed by communicating with the third port 42 through the throttle 62 and the fourth hole 59.
【００１６】次に作動を説明する。図３に示す状態より
スプール４３が第１圧力室４４内の自己の負荷圧Ｐ1 で
右方に押され、そのストロークがＳとなると受圧室５２
がロードピストン５１の小径部５８に開口して内部通路
６１によって第２ポート４１が第２圧力室４５に連通
し、第２圧力室４５にポンプ吐出圧Ｐ0 が作用してスプ
ール４３が減圧作動（左方に摺動して弁３６を遮断方向
に押す）して第１圧力室４４内の自己の負荷圧Ｐ1 と第
２圧力室４５内の圧力が等しくなった位置でスプール４
３が停止する。Next, the operation will be described. From the state shown in FIG. 3, when the spool 43 is pushed rightward by its own load pressure P 1 in the first pressure chamber 44 and its stroke becomes S, the pressure receiving chamber 52
Is opened to the small diameter portion 58 of the load piston 51, the second port 41 communicates with the second pressure chamber 45 by the internal passage 61, the pump discharge pressure P 0 acts on the second pressure chamber 45, and the spool 43 is depressurized. (Sliding to the left and pushing the valve 36 in the shut-off direction), the spool 4 is moved to a position where the own load pressure P 1 in the first pressure chamber 44 and the pressure in the second pressure chamber 45 become equal.
3 stops.
【００１７】前記第２圧力室４５内の圧油は絞り６２、
第４孔５９、第２小径部６０より第３ポート４２に流出
して負荷圧検出路１７に流れるが、この負荷圧検出路１
７は絞り２５でタンク２６に接続しているために絞り６
２の前後に差圧が生じ、負荷圧ＰLSが第２圧力室４５の
圧力よりも低圧となる。The pressure oil in the second pressure chamber 45 is a throttle 62,
Although it flows from the fourth hole 59 and the second small diameter portion 60 to the third port 42 and flows to the load pressure detection path 17, the load pressure detection path 1
7 is an aperture 25, which is connected to the tank 26.
A differential pressure occurs before and after 2, and the load pressure P LS becomes lower than the pressure in the second pressure chamber 45.
【００１８】このようであるから、アクチュエータがス
トロークエンドになって負荷圧Ｐ1とポンプ吐出圧Ｐ0
が等しくなって第２圧力室４５内の圧力がポンプ吐出圧
Ｐ0となった時に第３ポート４２に出力される負荷圧Ｐ
LSはポンプ吐出圧Ｐ0 よりも絞り６２の径に見合うだけ
低圧となる。Because of this, the actuator reaches the stroke end and the load pressure P 1 and the pump discharge pressure P 0 are reached.
Becomes equal and the pressure in the second pressure chamber 45 reaches the pump discharge pressure P 0 , the load pressure P output to the third port 42.
LS is lower than the pump discharge pressure P 0 by an amount commensurate with the diameter of the throttle 62.
【００１９】したがって、図２に示す油圧回路とした場
合に１つのアクチュエータがストロークエンドになって
も負荷圧検出路１７内の負荷圧ＰLSがポンプ吐出圧Ｐ0
より低圧となるから、ストロークエンドに達しない他の
アクチュエータに接続した圧力補償弁の減圧弁部６３の
第２圧力室４５内の圧力はポンプ吐出圧Ｐ0 より低圧と
なって弁３６が入口ポート３４のポンプ吐出圧Ｐ0 によ
って連通方向に押されて入口ポート３と出口ポート３５
を閉じることがなく、他のアクチュエータにポンプ吐出
圧油を供給できる。Therefore, when the hydraulic circuit shown in FIG. 2 is used, even if one actuator reaches the stroke end, the load pressure P LS in the load pressure detection path 17 is the pump discharge pressure P 0.
Since the pressure becomes lower, the pressure in the second pressure chamber 45 of the pressure reducing valve portion 63 of the pressure compensating valve connected to the other actuator that does not reach the stroke end becomes lower than the pump discharge pressure P 0 and the valve 36 becomes the inlet port. The inlet port 3 and the outlet port 35 are pushed by the pump discharge pressure P 0 of 34 in the communication direction.
The pump discharge pressure oil can be supplied to other actuators without closing.
【００２０】また、絞り６２の径を変更することで第２
圧力室４５内の圧力と負荷圧ＰLSとの圧力差を任意に変
更できるから、圧力補償弁の圧力補償特性を任意にもの
にできてアクチュエータの制御性能を向上できる。Further, by changing the diameter of the diaphragm 62, the second
Since the pressure difference between the pressure in the pressure chamber 45 and the load pressure P LS can be changed arbitrarily, the pressure compensation characteristic of the pressure compensation valve can be made arbitrary and the control performance of the actuator can be improved.
【００２１】[0021]
【発明の効果】第２圧力室４５内の圧油は絞り６２を通
って負荷圧検出路１７に流出し、その圧油の一部は負荷
圧検出路１７の絞り２５を経てタンク２６に流出するか
ら絞り６２の前後に圧力差が生じ、負荷圧検出路１７の
負荷圧ＰLSは第２圧力室４５の圧力よりも低圧となる。
したがって、１つの油圧ポンプの吐出圧油を複数の方向
制御弁によって各アクチュエータに供給する油圧回路に
おける各方向制御弁の入口側に圧力補償弁をそれぞれ設
け、その各負荷圧検出路１７を連通して各圧力補償弁が
最も高い負荷圧によってセットされるようにした場合
に、１つのアクチュエータがストロークエンドになって
ポンプ吐出圧Ｐ0 と自己の負荷圧Ｐ1 が等しくなっても
負荷圧ＰLSがポンプ吐出圧Ｐ0 より低くなるからストロ
ークエンドに達しない他のアクチュエータの圧力補償弁
における減圧弁部６３の第２圧力室４５内の圧力はポン
プ吐出圧Ｐ0 より低圧となり、その圧力補償弁のチェッ
ク弁部の弁３６が閉じることがないので他のアクチュエ
ータにポンプ吐出圧油を供給できる。The pressure oil in the second pressure chamber 45 flows out to the load pressure detection passage 17 through the throttle 62, and a part of the pressure oil flows to the tank 26 via the throttle 25 in the load pressure detection passage 17. Therefore, a pressure difference occurs before and after the throttle 62, and the load pressure P LS of the load pressure detection path 17 becomes lower than the pressure of the second pressure chamber 45.
Therefore, a pressure compensating valve is provided at the inlet side of each directional control valve in the hydraulic circuit that supplies the pressure oil discharged from one hydraulic pump to each actuator by a plurality of directional control valves, and each load pressure detection path 17 is communicated therewith. When each pressure compensation valve is set by the highest load pressure, even if one actuator reaches the stroke end and the pump discharge pressure P 0 and its own load pressure P 1 become equal, the load pressure P LS Is lower than the pump discharge pressure P 0, the pressure in the second pressure chamber 45 of the pressure reducing valve portion 63 of the pressure compensating valve of the other actuator that does not reach the stroke end becomes lower than the pump discharge pressure P 0 , and the pressure compensating valve Since the valve 36 of the check valve section of 1 does not close, the pump discharge pressure oil can be supplied to other actuators.
【図１】従来の圧力補償弁の断面図である。FIG. 1 is a sectional view of a conventional pressure compensation valve.
【図２】その圧力補償弁を用いた油圧回路図である。FIG. 2 is a hydraulic circuit diagram using the pressure compensation valve.
【図３】本発明の圧力補償弁の実施例を示す断面図であ
る。FIG. 3 is a sectional view showing an embodiment of the pressure compensation valve of the present invention.
１７…負荷圧検出路、１８…油圧ポンプ、１９…吐出
路、２５…絞り、２６…タンク、３１…弁本体、３４…
入口ポート、３５…出口ポート、３５…弁、３８…チェ
ック弁部、４０…第１ポート、４１…第２ポート、４２
…第３ポート、４３…スプール、４４…第１受圧室、４
５…第２受圧室、４７…ばね、６１…内部通路、６２…
絞り、６３…減圧弁部。17 ... Load pressure detection path, 18 ... Hydraulic pump, 19 ... Discharge path, 25 ... Throttle, 26 ... Tank, 31 ... Valve body, 34 ...
Inlet port, 35 ... Outlet port, 35 ... Valve, 38 ... Check valve part, 40 ... First port, 41 ... Second port, 42
... third port, 43 ... spool, 44 ... first pressure receiving chamber, 4
5 ... 2nd pressure receiving chamber, 47 ... Spring, 61 ... Internal passage, 62 ...
Throttle, 63 ... Pressure reducing valve section.
Claims (2)
入口ポート３４と方向制御弁１４の入力側に接続される
出口ポート３５の開口面積を制御する弁３６を有するチ
ェック弁部３８と、 第１圧力室４４に供給される自己の負荷圧Ｐ1 によって
前記弁３６の開口面積増方向の摺動を許容する一方向に
摺動し、第２圧力室４５内の圧力で前記弁３６を開口面
積減方向に押す他方向に摺動するスプール４３と、この
スプール４３の内部に形成され、スプール４３が一方向
に所定ストローク以上摺動した時に前記第２圧力室４５
に油圧ポンプ１８の吐出圧油を供給する内部通路６１
と、この内部通路６１を、絞り２５でタンク２６に接続
した負荷圧検出路１７に連通する絞り６２より成る減圧
弁部６３より構成したことを特徴とする圧力補償弁。1. A check valve portion 38 having a valve 36 for controlling an opening area of an inlet port 34 to which hydraulic oil discharged from a hydraulic pump 18 is supplied and an outlet port 35 connected to an input side of a directional control valve 14, The self-load pressure P 1 supplied to the first pressure chamber 44 causes the valve 36 to slide in one direction that allows sliding in the direction of increasing the opening area, and the pressure in the second pressure chamber 45 causes the valve 36 to move. A spool 43 that slides in the other direction that pushes in the direction of decreasing the opening area, and a second pressure chamber 45 that is formed inside this spool 43 and that is formed when the spool 43 slides in one direction for a predetermined stroke or more.
An internal passage 61 for supplying the discharge pressure oil of the hydraulic pump 18 to the
And a pressure reducing valve section 63 comprising a throttle 62 communicating with the load pressure detecting path 17 connected to the tank 26 by the throttle 25.
３１に、相対向して摺動自在に設け、その弁３６がスプ
ール４３側に所定ストローク摺動すると入口ポート３４
と出口ポート３５が開口し、スプール４３は第１圧力室
４４の圧力で弁３６より離れる一方向に摺動し、かつ第
２圧力室４５の圧力で弁３６に向う他方向に摺動するよ
うにし、 前記弁本体３１に油圧ポンプ１８の吐出路１９に接続し
たポートを形成し、前記スプール４３の内部通路６１は
スプール４３が所定ストローク一方向に摺動すると前記
ポートと第２圧力室４５を連通するようしたことを特徴
とする請求項１記載の圧力補償弁。2. The valve 36 and the spool 43 are slidably provided on the valve body 31 so as to face each other, and the inlet port 34 is provided when the valve 36 slides toward the spool 43 for a predetermined stroke.
And the outlet port 35 is opened so that the spool 43 slides in one direction away from the valve 36 by the pressure of the first pressure chamber 44 and slides in the other direction toward the valve 36 by the pressure of the second pressure chamber 45. And a port connected to the discharge passage 19 of the hydraulic pump 18 is formed in the valve body 31, and the internal passage 61 of the spool 43 connects the port and the second pressure chamber 45 when the spool 43 slides in one direction of a predetermined stroke. The pressure compensating valve according to claim 1, wherein the pressure compensating valve is in communication.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15992694A JP3534324B2 (en) | 1994-07-12 | 1994-07-12 | Pressure compensating valve |
| CN95194087A CN1152950A (en) | 1994-07-12 | 1995-07-11 | Pressure compensation valve |
| EP95924537A EP0771951A4 (en) | 1994-07-12 | 1995-07-11 | Pressure compensating valve |
| US08/750,876 US5735311A (en) | 1994-07-12 | 1995-07-11 | Pressure compensation valve |
| PCT/JP1995/001377 WO1996001951A1 (en) | 1994-07-12 | 1995-07-11 | Pressure compensating valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15992694A JP3534324B2 (en) | 1994-07-12 | 1994-07-12 | Pressure compensating valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0828506A true JPH0828506A (en) | 1996-02-02 |
| JP3534324B2 JP3534324B2 (en) | 2004-06-07 |
Family
ID=15704176
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15992694A Expired - Lifetime JP3534324B2 (en) | 1994-07-12 | 1994-07-12 | Pressure compensating valve |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US5735311A (en) |
| EP (1) | EP0771951A4 (en) |
| JP (1) | JP3534324B2 (en) |
| CN (1) | CN1152950A (en) |
| WO (1) | WO1996001951A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7717934B2 (en) | 2002-06-14 | 2010-05-18 | Ev3 Inc. | Rapid exchange catheters usable with embolic protection devices |
| ES2536082T3 (en) * | 2011-03-22 | 2015-05-20 | Parker-Hannifin Corporation | Pilot operated electroproportional mushroom valve with pressure compensation |
| CN103047212B (en) * | 2013-01-08 | 2015-04-01 | 刘安民 | Hydraulic control reversing valve |
| US10323762B2 (en) * | 2016-04-21 | 2019-06-18 | Parker-Hannifin Corporation | Three-way pressure control and flow regulator valve |
| CN113389829B (en) * | 2021-06-10 | 2022-09-30 | 徐州徐工矿业机械有限公司 | Mining dump truck and brake automatic compensator, brake and braking method thereof |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3321483A1 (en) * | 1983-06-14 | 1984-12-20 | Linde Ag, 6200 Wiesbaden | HYDRAULIC DEVICE WITH ONE PUMP AND AT LEAST TWO OF THESE INACTED CONSUMERS OF HYDRAULIC ENERGY |
| JP2916955B2 (en) * | 1991-01-31 | 1999-07-05 | 株式会社小松製作所 | Pressure compensation valve |
| US5533334A (en) * | 1992-04-08 | 1996-07-09 | Kabushiki Kaisha Komatsu Seisakusho | Pressurized fluid supply system |
-
1994
- 1994-07-12 JP JP15992694A patent/JP3534324B2/en not_active Expired - Lifetime
-
1995
- 1995-07-11 US US08/750,876 patent/US5735311A/en not_active Expired - Lifetime
- 1995-07-11 CN CN95194087A patent/CN1152950A/en active Pending
- 1995-07-11 EP EP95924537A patent/EP0771951A4/en not_active Withdrawn
- 1995-07-11 WO PCT/JP1995/001377 patent/WO1996001951A1/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| WO1996001951A1 (en) | 1996-01-25 |
| EP0771951A1 (en) | 1997-05-07 |
| US5735311A (en) | 1998-04-07 |
| CN1152950A (en) | 1997-06-25 |
| EP0771951A4 (en) | 1997-10-01 |
| JP3534324B2 (en) | 2004-06-07 |
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